JPS60208649A - Power unit mounting device containing liquid - Google Patents
Power unit mounting device containing liquidInfo
- Publication number
- JPS60208649A JPS60208649A JP6330084A JP6330084A JPS60208649A JP S60208649 A JPS60208649 A JP S60208649A JP 6330084 A JP6330084 A JP 6330084A JP 6330084 A JP6330084 A JP 6330084A JP S60208649 A JPS60208649 A JP S60208649A
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- fluid
- chamber
- damping force
- orifices
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like
- F16F13/105—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers
- F16F13/107—Passage design between working chambers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
この発明は、流体入りパワーユニットマウント装置に関
するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid-filled power unit mounting device.
(従来技術)
従来の流体入シパワーユニットマウント装置として、例
えば第1図に示すようなものがある(特開昭58−72
741号)。すなわち、パワーユニット側の基板51と
車体側の基板52との間に流体を封入させた内部空間5
3aを有するマウントラノ?−53を固着し、一方の基
板52側にダイヤフラム54と仕切板55とを取付けて
、ダイヤフラム54と仕切板55との間に副次室56を
形成し、仕切板55と他方の基板51との間に流体室5
7を形成し、該副次室56と流体室57とに流体を封入
させ、かつ仕切板55に一対のオリフィス58.59を
設け、該オリフィス58.59にて流体室57と副次室
56とを連通させたものである。(Prior Art) As a conventional fluid-filled power unit mounting device, there is one shown in FIG.
No. 741). That is, an internal space 5 in which fluid is sealed between a board 51 on the power unit side and a board 52 on the vehicle body side.
Mt Lano with 3a? -53 is fixed, and a diaphragm 54 and a partition plate 55 are attached to one side of the substrate 52, a subchamber 56 is formed between the diaphragm 54 and the partition plate 55, and a subchamber 56 is formed between the diaphragm 54 and the partition plate 55, and fluid chamber 5 between
A pair of orifices 58,59 are provided in the partition plate 55, and the orifices 58,59 allow the fluid chamber 57 and the secondary chamber 56 to be sealed. It is a communication between
しかしながら、このような従来のマウント装置にあって
は、一対のオリフィス58.59は、一方のオリフィス
58の断面積をA′1、他方のオリフィス59の断面積
をA/2としてA’ 1 / A′2 :4、また一方
のオリフィス58の長さをt′3、径f d’t 、他
方のオリフィス59の長さを71、径8d′! として
Z/ 、/ dtl・d’ t/ Z t : 2の関
係となっており、大きな断面積A’ Hのオリフィス5
8のロスファクタか0.3程度と低く、小さな断面ut
A’t のオリフィス59のロスファクタはさらにそ
のl/4程度と低く、エンジンシェイクを生ずる低周波
数域例えば5〜15Hzにおいて良好な減衰力を発生さ
せることが困難であるという問題点かあった。However, in such a conventional mounting device, the pair of orifices 58 and 59 have a cross-sectional area of A'1/A'1, and a cross-sectional area of A'1 and A/2 of the other orifice 59, respectively. A'2: 4, and the length of one orifice 58 is t'3 and diameter f d't, and the length of the other orifice 59 is 71 and diameter 8d'! As Z/ , / dtl・d' t/ Z t : 2, the orifice 5 with a large cross-sectional area A' H
Low loss factor of 8 or around 0.3, small cross section ut
The loss factor of the orifice 59 of A't is still as low as about 1/4, and there is a problem in that it is difficult to generate a good damping force in the low frequency range where engine shake occurs, for example, 5 to 15 Hz.
(発明の目的)
この発明は、このような従来の問題点に鑑みてなされた
もので、本発明者等の行なった種々の実験から知得され
た後記する事実に基づき、マウント装置に、流体室と副
次室とを連通させる断面積のほぼ等しい複数個のオリフ
ィスを備えさせ、その一対のオリフィスの長さ比if
15〜9に設定させることにより、減荻力か最大値を示
す周波数をエンジンシェイクを生ずる低周波数域に合致
させ、かつ適正な減衰力を発生させ、上記問題点を解決
することを目的としている。(Object of the Invention) This invention was made in view of such conventional problems, and is based on the facts described later that were learned from various experiments conducted by the present inventors. A plurality of orifices having approximately equal cross-sectional areas are provided to communicate the chamber and the sub-chamber, and the length ratio of the pair of orifices is
By setting the damping force to 15 to 9, the purpose is to match the frequency showing the maximum value of the engine shake to the low frequency range that causes engine shake, and generate an appropriate damping force, thereby solving the above problems. .
(実施例)
以下、この発明について図示の実施例を参照して説4明
する。(Embodiments) The present invention will be explained below with reference to illustrated embodiments.
第2図に、この発明の第−実施例を示す。パワーユニッ
ト側の基板1と単体側の基板2との間に内部空間3ai
有するマウントラバー3を固着し、各基板1,2側にダ
イヤフラム4.5と仕切板6,7とを各々固定し、一方
のダイヤフラム49111 K第−副次室8を形成し、
他方のダイヤフラム5側に第二副次室98形成しである
。FIG. 2 shows a second embodiment of the invention. An internal space 3ai is provided between the power unit side board 1 and the single unit side board 2.
The mount rubber 3 having the diaphragm 49111K is fixed, and the diaphragm 4.5 and the partition plates 6 and 7 are fixed to each of the substrates 1 and 2, and one diaphragm 49111K is formed to form a secondary chamber 8.
A second subchamber 98 is formed on the other diaphragm 5 side.
具体的には、マウントラバー3は、仕切板6と円錐蟻状
の支持板10との間に加硫接着され、仕切板6はダイヤ
フラム4の外縁ヲ挾圧させてその外縁を内114+1に
折曲げて基板1に固定され、支持板lOは、その下部を
基板2に固定されて基板2と一体を成して仕切板7とダ
イヤフラム5の各外周縁を秋眉している。かくしてダイ
ヤフラム4と仕切板6とに′7C第−副次室8を画成し
、側仕切板6,7間に流体歴118形成し、仕切板7と
ダイヤフラム5とにて第二副次室9を画成し、各室8,
9.11に水、油等の非圧縮性の流体を封入しである。Specifically, the mount rubber 3 is vulcanized and bonded between the partition plate 6 and the conical dovetail-shaped support plate 10, and the partition plate 6 presses the outer edge of the diaphragm 4 and folds the outer edge into the inner part 114+1. The supporting plate 1O is bent and fixed to the substrate 1, and its lower part is fixed to the substrate 2, forming an integral part with the substrate 2 and surrounding the outer peripheral edges of the partition plate 7 and the diaphragm 5. Thus, the diaphragm 4 and the partition plate 6 define a '7C secondary chamber 8, a fluid history 118 is formed between the side partition plates 6 and 7, and the partition plate 7 and the diaphragm 5 define a second secondary chamber 8. 9, each room 8,
9.11 is filled with an incompressible fluid such as water or oil.
そして、一方の仕切板7には、流体室1.1と第二副次
室9とを連通させる絞り流路たるオリフィス14そ設け
、他方の仕切板6には、流体gliと第一副次室8とを
連通させる絞り流路たるオリフィス15を設ける。オリ
フィス14゜15は、第3図に示すように2字状の流路
14a。One partition plate 7 is provided with an orifice 14, which is a throttle flow path that communicates the fluid chamber 1.1 and the second subchamber 9, and the other partition plate 6 is provided with an orifice 14 that connects the fluid gli and the first subchamber 9. An orifice 15 serving as a throttle flow path communicating with the chamber 8 is provided. The orifices 14 and 15 are two-shaped flow passages 14a as shown in FIG.
15aよりなり一端の開口14b、15bにて流体室1
1に遅進させ、他端の開口15c 、 14cに°C第
一副次室8または第二副次室9に連通させである。The fluid chamber 1 is formed by openings 14b and 15b at one end.
1, and the openings 15c and 14c at the other end communicate with the first sub-chamber 8 or the second sub-chamber 9.
ここで、本発明者等が行なった実験により、下記の事実
が判明しでいる。すなわち、オリフィス14.15の減
其能力か最大値を示す周波数はオリフィス14.15の
長さtと径d(σ、ここにAは断面積)とに依存してお
り、l/σおよびd(4ズー)に比例する。また、減衰
能力は断面積Aに比例する0
しかして、両オリフィス14.15(7)′#、衰能力
を良好値すなわち減衰能力の目安として一般に用いられ
ているロスファクタを0.4以上として一致させて与え
るためには、一方のオリフィス14のロスファクタの最
大値f Llmax 1断面積fAlまた他方のオリフ
ィス15のロスファクタの最大値をLlmax 1断面
積をA!として、L1maX/Lama X ” At
/A、:= 1であり、従ってA、 = A、となる。As a result of experiments conducted by the present inventors, the following facts have been discovered. In other words, the frequency at which the orifice 14.15 exhibits the maximum value of its reduction ability depends on the length t and diameter d (σ, where A is the cross-sectional area) of the orifice 14.15, and l/σ and d (4 zoos). In addition, the damping capacity is proportional to the cross-sectional area A. Therefore, if both orifices are 14.15(7)'#, the damping capacity should be set to a good value, that is, the loss factor generally used as a guideline for the damping capacity should be set to 0.4 or more. In order to match, the maximum value of the loss factor of one orifice 14 f Llmax 1 cross-sectional area fAl and the maximum value of the loss factor of the other orifice 15 must be Llmax 1 cross-sectional area A! As, L1maX/Lama X ” At
/A, := 1, so A, = A.
また、一方のオリフィス14の減衰能力か最大値を示す
共振周波数をfL、max1長さをtい径゛をdl、ま
た、他方のオリフィス15の減衰能力が最大値を示す共
振周波数をf Llma X %長さをt6、径f d
t トして、エンジンシェイクを生ずる低周波数域例え
ば5〜15Hzにおいて、一方のオリフィス14の共振
周波数を8H2とし、他方のオリフィス15の共振周波
数を13H2とすれば、fL1max/ fLfnax
=’t/ a!′σシz’=; L 63、またA。In addition, the resonance frequency that indicates the maximum value of the damping capacity of one orifice 14 is fL, the length of max1 is t and the diameter is dl, and the resonance frequency that indicates the maximum value of the damping capacity of the other orifice 15 is f Llma % length t6, diameter f d
If the resonance frequency of one orifice 14 is 8H2 and the resonance frequency of the other orifice 15 is 13H2 in the low frequency range where engine shake occurs, for example 5 to 15Hz, then fL1max/fLfnax
='t/ a! 'σsiz'=; L 63, also A.
=痴よりd、= d、ゆえに、t、−2,641,とな
る。また、一方のオリフィス14の共振周波数を5H2
とし、他方のオリフィス15の共振周波数を15H2と
すれば、f L、+nax / f L2max =
dtl d2 ・Fレテ=3ゆえに、tt: 9 tl
となる。= d, = d, therefore, t, -2,641. In addition, the resonance frequency of one orifice 14 is set to 5H2.
If the resonance frequency of the other orifice 15 is 15H2, then f L, +nax / f L2max =
dtl d2 ・Frete=3, so tt: 9 tl
becomes.
しかして、dをほぼ同じにしてtを2.5〜9倍変える
必要がある。Therefore, it is necessary to keep d approximately the same and change t by 2.5 to 9 times.
次に作用について説明する。Next, the effect will be explained.
エンジンシェイクを生ずる低周波数域、例えば5〜13
H2での大振幅振動か基板lより入力されると、マウン
トラノ々−3か大きく伸粗し、流体室11の体積変化を
生ずる。その結果、低い周波数域においで長さの長いオ
リフィス14内の流体質量が共振して大きな減放力を発
生させ、それより高い周波数域において長さの短いオリ
フィス15内の流体質量が共振してほぼ同じ減衰力を発
生させ、エンジンシェイクを効果的に制振させる。Low frequency range that causes engine shake, e.g. 5-13
When large-amplitude vibrations at H2 are input from the substrate 1, the mount Rano-3 is greatly expanded and the volume of the fluid chamber 11 changes. As a result, the fluid mass in the long orifice 14 resonates in a low frequency range, generating a large release force, and the fluid mass in the short orifice 15 resonates in a higher frequency range. Generates almost the same damping force and effectively suppresses engine shake.
第4図に、この発明の第二実施例を示す。パワーユニッ
ト側の基板101と車体側の基板102との間に内部空
間1113a−i有するマウントラノ々−103を固層
し、一方の基板102側にダイヤフラム104と仕切板
107とを固定し、ダイヤフラム104と仕切板107
との間に副次室1098形成し、他方の基板101 (
11に流体室1117i:形成して副次室109と流体
室111とに流体を封入しである。具体的には、マウン
トラノ々−103は覆板106と円錐環状の支持板11
0との間に加硫接着され、覆板106は外周縁を基板1
01に溶接同治され、支持板110はその下部フランジ
を仕+J1板107、ダイヤフラム104と共に基:I
″]A02の外周縁に接着されている。FIG. 4 shows a second embodiment of the invention. A mount platen 103 having an internal space 1113a-i is solidly layered between the power unit side substrate 101 and the vehicle body side substrate 102, and a diaphragm 104 and a partition plate 107 are fixed to one side of the substrate 102. Partition plate 107
A subchamber 1098 is formed between the other substrate 101 (
A fluid chamber 1117i is formed in 11 and a fluid is sealed in the sub chamber 109 and the fluid chamber 111. Specifically, the mount lano-103 includes a cover plate 106 and a conical ring-shaped support plate 11.
0, and the cover plate 106 has an outer peripheral edge attached to the substrate 1.
01, and the support plate 110 has its lower flange fixed together with the J1 plate 107 and the diaphragm 104.
″] is glued to the outer peripheral edge of A02.
そして、仕切板107の流体室111側と副次室109
側とにはそれぞれ流体m1llと副次g109とを連通
させる絞り流路たるオリフィス114゜115を設ける
。オリフィス114 、115は、第5図に示すように
視ylx4d、 zxsd にて区画されたわん曲する
流路114a 、 115a よりなり一端の開口11
4b 、 115b にて流体室111に連通さぜ、細
端の開口114c 、 115c にて副次室109に
連通させである。Then, the fluid chamber 111 side of the partition plate 107 and the subchamber 109
Orifices 114 and 115 are provided on the sides, respectively, to serve as throttle channels for communicating the fluid m1ll with the subdivision g109. As shown in FIG. 5, the orifices 114 and 115 are curved channels 114a and 115a that are divided at ylx4d and zxsd, and the opening 11 at one end.
4b and 115b communicate with the fluid chamber 111, and narrow end openings 114c and 115c communicate with the subchamber 109.
シカシて、一方のオリフィス114の断面bt A3と
他方のオリフィス115の断面積A4とをほぼ等しくす
ると共に、一方のオリフィス114の長さをtl、他方
のオリフィス115の長さf t4として、’a/14
=2.5〜9の関係を与えである。In other words, the cross-sectional area btA3 of one orifice 114 and the cross-sectional area A4 of the other orifice 115 are approximately equal, and the length of one orifice 114 is tl, and the length of the other orifice 115 is ft4, 'a /14
=2.5 to 9 is given.
しかして、この実施例によっても前記実施例と同様の作
用か得られる。Therefore, this embodiment also provides the same effect as the previous embodiment.
なお、オリフィス114,115は上記構成に限定され
るものではなく、第6図に示すようにうず巻状の流路1
16aの両端に開口116b 、 116cを設けたオ
リフィス116とすることもできる。Note that the orifices 114 and 115 are not limited to the above configuration, and as shown in FIG.
The orifice 116 may be provided with openings 116b and 116c at both ends of the orifice 16a.
またオリフィス114の共振周波数を例えば5Hzに設
定し、オリフィス115の共振周波数を例えば15 H
zに設定し、史に共振周波数か10Hzのオリフィスを
仕切板IC)7に設けることもできる。Further, the resonant frequency of the orifice 114 is set to, for example, 5Hz, and the resonant frequency of the orifice 115 is set to, for example, 15Hz.
z, and an orifice with a resonant frequency of 10 Hz can be provided in the partition plate IC)7.
(発明の構成)
以上説明したように、この発明によればその構成を、ノ
ξワーユニット偵11の基板と車体側の基板との間に内
部空間を有するマウントラノ々−を固ンi) L/、少
なくとも一方の基板側にダイヤフラムと仕切板とを取付
けで、ダイヤフラムと仕切板との間に副次室を形成し、
他方の基板側に流体室を形成して、該副次室と流体室と
に流体を封入すると共に、上記仕切板は、流体室と副次
室とを連通させ、断面積がほぼ等しく、かつ一対の長さ
比か25〜9に設定されたオリフィスを復数個備える流
体入りパワーユニットマウント装置とした。(Configuration of the Invention) As explained above, according to the present invention, the configuration is such that the mount planes having an internal space between the base plate of the lower unit 11 and the base plate on the vehicle body side are fixed. /A diaphragm and a partition plate are attached to at least one substrate side, and a subchamber is formed between the diaphragm and the partition plate,
A fluid chamber is formed on the other substrate side, and a fluid is sealed in the sub-chamber and the fluid chamber, and the partition plate communicates between the fluid chamber and the sub-chamber, has approximately equal cross-sectional area, and The fluid-filled power unit mount device is provided with a plurality of orifices having a pair length ratio of 25 to 9.
(発明の、効果)
従って、オリフィスの断面02 (E” :11″!桶
に設定することにより、減衰能力をほぼ同一の良好値に
設定させ、刀)つそれらの共振周波数をエンジンシェイ
クを生ずる低周波数域に設定させて、エンジンシェイク
を効果的に制像させることかできるという効果が得られ
る。(Effects of the invention) Therefore, by setting the cross section of the orifice to 02 (E": 11"), the damping capacity can be set to almost the same good value, and the resonance frequency of the orifice can be adjusted to cause engine shake. By setting it in a low frequency range, it is possible to effectively suppress engine shake.
第1図は従来のマウント装置の断面図、第2図はこの発
明の第一実施1りuを示すlυI而図面第3図はオリフ
ィスの断面図、第4図はこの発明の第二実施例を示す断
面図、εB5図はオリフィスの断面図、第6図はオリフ
ィスの他の構造例を示す断面図である。
1.101,2.102 :基板、3,103 :マウ
ントラノ々−13a、1113a :内部空間、4,5
,104 :ダイヤフラム、6,7,107 :仕切板
、8,9,109 :副次室、11.111:流体室、
14,15,114.115 ニオリフイス代理人 弁
理士 前 1)利 之
第1図
58″:)9 Ob O’)
第2図
第3図
第4図
115c 115a
第5図
第6図
116CFig. 1 is a sectional view of a conventional mounting device, Fig. 2 is a drawing showing a first embodiment of the present invention, Fig. 3 is a sectional view of an orifice, and Fig. 4 is a second embodiment of the invention. Figure εB5 is a cross-sectional view of the orifice, and FIG. 6 is a cross-sectional view showing another structural example of the orifice. 1.101, 2.102: Substrate, 3,103: Mount Rano-13a, 1113a: Internal space, 4,5
, 104: Diaphragm, 6, 7, 107: Partition plate, 8, 9, 109: Sub-chamber, 11.111: Fluid chamber,
14, 15, 114.115 Niorifis agent Patent attorney front 1) Toshiyuki Figure 1 58'':) 9 Ob O') Figure 2 Figure 3 Figure 4 115c 115a Figure 5 Figure 6 116C
Claims (1)
内部空間を有するマウントラノ々−を固着し、少なくと
も一方の基板側にダイヤフラムと仕切板とを取付けて、
ダイヤフラムと仕切板との間に副次室を形成し、他方の
基板側に流体室を形成して、該副次室と流体室とに流体
を封入すると共に、上記仕切板は、流体室と副次室とを
連通させ、断面積がほぼ等しく、かつ一対の長さ比が2
.5〜9に設定されたオリフィスを複数個備えることを
特徴とする流体入りノぞワーユニットマウント装置。1. Fix a mount plate having an internal space between the board on the side of the noswer unit and the board on the vehicle body side, and attach a diaphragm and a partition plate to at least one board side,
A sub-chamber is formed between the diaphragm and the partition plate, a fluid chamber is formed on the other substrate side, and a fluid is sealed in the sub-chamber and the fluid chamber. communicate with the secondary chamber, have approximately the same cross-sectional area, and have a length ratio of 2.
.. A fluid-filled nozzle unit mount device comprising a plurality of orifices set in the range of 5 to 9.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6330084A JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6330084A JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS60208649A true JPS60208649A (en) | 1985-10-21 |
Family
ID=13225318
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP6330084A Pending JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60208649A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5145156A (en) * | 1990-02-02 | 1992-09-08 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mount having two differently tuned orifices selectively utilized for damping or isolating vibrations in different frequency ranges |
US5286012A (en) * | 1992-05-07 | 1994-02-15 | Hutchinson | Hydraulic antivibration devices |
-
1984
- 1984-04-02 JP JP6330084A patent/JPS60208649A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5145156A (en) * | 1990-02-02 | 1992-09-08 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mount having two differently tuned orifices selectively utilized for damping or isolating vibrations in different frequency ranges |
US5286012A (en) * | 1992-05-07 | 1994-02-15 | Hutchinson | Hydraulic antivibration devices |
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